Engine



K. F. ZIEGLER Feb. 22, 1966 ENGINE Filed July 9, 1962 3 Sheets-Sheet 1 INVENTOR. (Aer I Z5615? \tm JrrmFA FYL K. F. ZIEGLER Feb. 22, 1966 ENGINE 3 Sheets-Sheet 2 Filed July 9, 1962 m R Wm W E 0 v6 r N; r 15 W i K. F. ZIEGLER Feb. 22, 1966 ENGINE 3 Sheets-Sheet 5 Filed July 9, 1962 INVENTOR. X wer E Z 61 6 BY United States Patent 3,236,218 ENGINE Kurt F. Ziegler, Zion, 11]., assiguor to Outboard Marine Corporation, Waukegan, Ill., a corporation of Delaware Filed July 9, 1962, Ser. No. 208,286 40 Claims. (Cl. 123-139) The invention relates generally to internal combustion engines. More particularly, the invention relates to multi-cylinder, internal combustion engines including an injection fuel supply system and an engine lubricating system including an arrangement for directly supplying oil to the engine cylinders.

The invention provides, in part, a multi-cylinder, two stroke engine including a fuel supply system including a fuel injection pump, and a separate lubrication system including pumping means for delivering measured quantities of lubricant to the cylinder -or crankcase. In the preferred embodiment, the fuel injection pump and the oil pump are driven, in co-ordination with the firing of spark plugs, from a common shaft which also serves to effect operation of a distributor.

The use of an injection fuel supply system coupled with a separate but related lubrication system for directly feeding measured quantities of oil from a storage reservoir to the crankcase or crankcases, particularly in a multi-cylinder, two stroke engine having a separate crankcase for each cylinder, provides several important advantages. First, the separate fuel supply and lubrication systems avoid the heretofore common necessity of premixing the fuel and oil. Second, supplying fuel directly to each cylinder, independently of the supply of combustion air, effect-s very substantial fuel economy because fuel is not Wasted during scavenging by a fuel-combustion air mixture. Third, improved lubrication is obtained, while also providing important oil savings. In this regard, substantially reduced amounts of oil are carried to the cylinder by the combustion air, thereby also substantially lessening the undesirable odor ordinarily associated with the exhaust from a two stroke engine, which odor is generally attributable to the presence of lubricating oil.

In the preferred embodiment, the fuel supply system includes a two-step pumping arrangement including the beforementioned fuel injection pump and an auxiliary fuel pump for delivering fuel from the fuel storage tanks to the injection pump. The injection pump provided by the invention includes a series of separate pump units, one for each engine cylinder, which pump units are arranged in parallel relation to each other in a radially arranged pattern about a common axis. The injection pump also includes a rotatable control rod which is located along said common axis and is operable to effect a common, simultaneous adjustment of the rate of fuel delivery from each pump unit. The control rod is rotatively reciprocable by a crank actuated by a vacuum control operable in response to the pressure condition in the combustion air intake. If desired, however, the control rod can be mechanically or manually controlled, or can be actuated by a combination of pressure responsive and manual means.

The oil supply system provided by the invention includes an oil pump which serves to deliver measured quantities of oil to each cylinder through separate oil conduits and oil supply fittings located in the cylinder Walls, preferably adjacent the bottom thereof. In the preferred embodiment, the fuel pump includes a rotatable element or rotor carrying a pair of piston members which are reciprocable in response to the rotation of said rotor and, in co-operation with such rotation, thereby serve to deliver measured quantities of oil to each of the separate conduits leading to the individual engine cylinders. Also 3,236,218 Patented Feb. 22, 1966 in the preferred embodiment, the pistons are located at the ends of the rotor and are actuated, at least in part, by camming surfaces adjacent the ends of the rotor.

In the preferred embodiment, the rotor also serves to operate the auxiliary fuel pump. Specifically, the rotor includes eccentric crank hubs carrying connecting rods actuating a pair of diaphragms operable to effect pumping of fuel from a fuel storage tank to the fuel injection pump.

In general, the invention also provides a compact association for a fuel injection pump and an oil pump, together with an oil circulating pump and an auxiliary fuel pump, all of which are driven by a common shaft.

Other objects and advantages of the invention will become known by reference to the following description and the accompanying drawings, in which:

FIGURE 1 is a partially diagrammatic, perspective view of an engine assembly 11 embodying various of the features of the invention;

FIGURE 2 is an enlarged fragmentary view, partially in section, taken transversely of the engine assembly shown in FIGURE 1;

FIGURE 3 is an enlarged fragmentary view, partially in section, of the fuel and oil pumping device included in the engine assembly shown in FIGURE 1, which view is taken generally along line 33 of FIGURE 4;

FIGURE 3a is an enlarged view of a portion of the fuel and pumping device shown in FIGURE 3;

FIGURE 4 is a sectional view, partially broken away, taken generally along line 44 of FIGURE 3;

FIGURE 5 is an enlarged sectional view of the air horn 43 shown in FIGURES 1 and 2;

FIGURE 6 is a fragmentary view, partially in section, taken along line 6-6 of FIGURE 5;

FIGURE 7 is a view, partially in section, of the pressure responsive means which is shown in FIGURE 1 and which controls the fuel discharge rate of the fuel injection pump;

FIGURE 8 is a fragmentary, sectional view taken generally along line 88 of FIGURE 4;

FIGURE 9 is a fragmentary, sectional view taken generally along line 99 of FIGURE 4;

FIGURE 10 is a fragmentary, sectional view taken generally along line 10-10 of FIGURE 4;

FIGURE 11 is a fragmentary, sectional view taken generally along line 1111 of FIGURE 3; and

FIGURE 12 is a fragmentary view, partially in section taken generally along line 1212 of FIGURE 10.

The engine unit or assembly 11, shown in FIGURE 1, comprises an internal combustion engine 13 together with related supporting components including, but not limited to, a fuel supply system including a fuel injection pump 17, a separate oil or lubricating system including an oil injection pump 21, and a distributor 23. The engine 13 is exemplary of various types of internal combustion engines which can be employed in engine assemblies incorporating various of the features of the invention. In particular, the engine 13 is a two stroke, spark ignition, V4 engine including an engine block 24 and is generally of well known construction, except as modified in accordance with the invention to the extent hereinafter described.

Each of the engine cylinders 25 (see FIGURE 2) forms one portion of a generally closed chamber 27 which also includes a crankcase 29. Reciprocally carried in each cylinder 25 is a piston 31 which is joined by a connecting rod 33 to a crankshaft 35 extending through each of the several crankcases 29. Each of the cylinders 25 also has ignition means, here represented by a conventional spark plug 37. Combustion air is admitted to each of the cylinders 25 from its connected crankcase 29 through a trans fer passage 39 which is opened and closed by piston movement. Entry of combustion air into the crankcases 29 and delivery thereof to the engine cylinders 25 through the transfer passage 39 results in the conventional manner from reciprocation of the pistons, which reciprocation pressurizes the atmosphere in the crankcases during piston movement from top dead center to bottom dead center, and creates a sub-atmospheric pressure in the crankcases during movement in the opposite direction. Combustion air is admitted to the crankcase through conventional reed valves 41 communicating, in accordance with the invention, with a valve housing or air horn 43 having a throttle valve 45. The construction of the air horn 43 and its co-operation with the fuel supply system will be described in greater detail hereinafter.

Various distributor constructions can be employed and, in the dis-closed construction, the distributor 23 is actuated by an auxiliary driveshaft 47 (see FIGURE 3) which is carried in generally parallel relation to the crankshaft 35 and driven by suitable means, such as a timing belt 49 (see FIGURE 1) to insure a constant rotational relation between the auxiliary driveshaft 47 and the crankshaft 35. In turn, the distributor 23 is connected in the usual fashion to each of the spark plugs 37 so as to obtain the desired firing order.

In accordance with the invention, each of the cylinders 25 also has mounted thereon a fuel injection nozzle 51 (see FIGURE 2), each of which is, in turn, connected by separate suitable conduit means, such as nylon tubes 53, to the fuel injection pump 17. Each of the cylinders 25 also has mounted thereon an oil fitting 55 (see FIGURE 2) which communicates with the interior of the associated cylinder adjacent the bottom thereof. Each of the oil fittings 55 connected through separate suitable conduit means, such as nylon tubes 57, to the oil injection pump 21.- As will be seen hereinafter, the auxiliary driveshaft 47 also serves to drive the fuel injection pump 17 and the oil injection pump 21,

Fuel supply system (see FIGURE 4) which communicates through a fuel supply conduit 113 with a source of fuel, i.e., a fuel storage tank or tanks (not shown) and which supplies fuel through a conduit system, to be described, to the fuel injection pump 17. The fuel supply system also includes a filtef 115 (see FIGURE 3) between the auxiliary 'iurri'p' 111 and the injection pump 17, which filter assures the exclusion of unwanted grit or impurities from the injection pump 17 and from the injection nozzles 51. A fuel return conduit 117 (see FIGURE 3) connects the fuel injecting pump 17 and the fuel storage tank.

Fuel injection pump The fuel injection plmp 17 includes a main or oil pump housing 151 which is suitably supported from the engine block 24, as by brackets 153 (see FIGURES 1 and'2). The main housing 151 supports the distributor 23, includes a bore 154 and bearings 156 (only one shown) for the auxiliary driveshaft 47, and supports a fuel injection housing 155 incorporating four generally identical pump units 157. Each pump unit 157 is generally of conventional construction and includes a sleeve or liner 159 having a cylindrical bore 161 and a piston 163 reciprocable axially within the bore 161. Each piston 163 and its associated sleeve 159 are oscillatable relative to one another to vary the fuel discharge rate.

The fuel injection pump 17 also includes means, including the before-mentioned auxiliary driveshaft 47 and a timing cam 165, for axially reciprocating the pistons 163 in timed relation to firing of the spark plugs 37, i.e., so that fuel is injected in the associated one of the engine cylinders during piston movement therein from bottom dead center to top dead center. Also included in the fuel injection pump 17 is means for effecting common oscillation of all of the sleeves 159 relative to their associated pistons 163 to effect like variation in the fuel discharge rate from each of the pump units 157 in response to reciprocation of the pistons 163.

More particularly, the fuel injection housing includes an elongated central bore 167 which communicates through a sealed transverse recess 169 with each of four generally identical elongated cavities 171 disposed parallel to the central bore 167, at a common radius or distance therefrom, and in equiangular relation to each other about the bore 167. Each of the cavities 171 contains one of the pump units 157. The central bore 167 also communicates with an oil supply port 173 and forms a part of the lubricating supply system still to be described. The injection pump housing 155 also includes a fuel inlet port 175 communicating with a fuel reservoir 177 defined, in part, by an enlarged annular portion 179 of each cavity 171. Also provided in the fuel injection housing 155 is means including a port 181 and a check valve 183 for providing communication with the fuel return conduit 117 leading to the fuel storage tank so as to permit fuel flow to the storage tank in response to the development of excessive pressure in the fuel reservoir 177.

The pumping unit sleeves 159 each include a stepped outer surface, a portion of which is rotatably received by the associated one of the cavities 171. Another portion of the outer surface of each sleeve 159 co-operatesv with the associated enlarged cavity portion 179 to define the fuel reservoir 177. At its upper end, each sleeve 159 has connected thereto a gear 185 which extends within the transverse recess 169 and is meshed with a gear 187 on a control rod 189 so as to effect a common rotation of all of the sleeves'159 relative to the associated pistons 163 incident to rotation of the control rod. The control rod 189 is coupled to the air born 43 for actuation in a mannerstill to be described.

Each of the cylindrical bores 161 in the sleeves 159 extends parallel to the central bore 167 of the injection pump housing 155. Each sleeve 159 includes a main. fuel port 191 which communicates with the associated enlarged annular cavity portion 179 and permits fuel flow between the'fuel reservoir 177' and the cylindrical bore: 161. An auxiliary fuel port 193 through each sleeve. 159 to the fuel reservoir 177 is also provided.

Fixed in each of the cavities 171, beneath the associated sleeve 159' and in communication with the cylindrical bore 161, is a suitable fitting 195 which includes a check. valve 197 and is connected to the associated one of the. tubes 53 leading to the associated engine cylinder 25.

Each piston or plunger 163 is an elongated, generally cylindrical member having,,at its upper end, a head 199 and on the outer cylindrical surface, adjacent its lowerend, is provided with a recess 201 which co-operates with: the main fuel port 191 and auxiliary fuel port 193 in; the associated sleeve 159 to regulate fuel flow. More: particularly, the recess 201 is conventionally constructed. and includes an upper edge having a major portion 203' of spiral formation, which portion 203 is rotatably shift-- able, as is known, relative to the main fuel inlet port 191,. incident to oscillation of the associated sleeve 159, vwhere-- by closing of the main fuel port occurs during reciprocation of the piston 163 at various times, depending on the angular relation of the piston to the sleeve. As a: result, quantitative control of the fuel flow from thecylindrical bore 161 through the check valve 197 and to the engine cylinders 25 is achieved.

Each of the pistons 163 is reciprocable in the associated cylindrical bore 161 to force fuel at a high pressure through the associated check valve 197 by means which, in the disclosed construction, also serve to prevent angular movement of the piston about its axis. As a result, when the control rod 189 is rotated, all of the sleeves 159 rotate in unison relative to their associated pistons 163.

The piston reciprocation means includes separate follower assemblies 205 at the upper end of each of the cavitics.171, each'of'which assemblies is attached to the associated one of the pistons 163 to prevent piston rotation while effecting piston reciprocation. More particularly, each follower assembly 205 includes a reciprocably seated bushing 207 which supports a shaft 209 extending diametrically of the associated cavity and radially of the central bore 167. Mounted on each of the shafts 209 is a follower in the form of a roller 211. Rotation of the bushing 207 relative to its associated cavity 191 is prevented by a key 212 (see FIGURE 3a) extending into an axially extending slot 213 in the bushing. In the disclosed construction, the key 212 is provided by a projection at the end of a screw 215 (see FIGURE 3) threaded in the injection pump housing 155 in radially extending relation to the axis of the associated cavity 171. Action of the key 212 in the slot 213 also serves to limit reciprocation of the associated follower assembly 205.

Carried by each of the bushings 207 beneath the roller 211 is a transverse element 217 which is connected to the head 199 of the associated piston 163 and to the bushing 207 by suitable means preventing relative rotation between the bushing 207 and the piston head 199. Each of the bushings 207 is urged outwardly of the associated cavity 171, to the extent permitted by engagement of the key 212 in the slot 213, by a coil spring 219 which surrounds the upper end of the associated piston 163 and is confined between a seat 221 on the lower face of the transverse element 217 and an annular seat 223 emplaced against an annular shoulder in the associated cavity 171.

Movement of the pistons 163 inwardly of their respective sleeves 159 to effect fuel injection into the associated engine cylinders 25 in timed relation to the firing of the spark plugs 37 is provided by means including the timing cam 165 which is housed in a cavity or recess 225 in the main housing 151 and is mounted at the end of the auxiliary driveshaft 47. Incident to rotation of the auxiliary driveshaft, the timing cam 165 engages the rollers 211 to press the follower assemblies 205 inwardly of the cavities 171 against the action of the springs 219 and to thereby displace the pistons 163 axially of the cylindrical bores 161 to discharge measured quantities of fuel into the tubes 53 leading to the engine cylinders 25.

Control rod actuating means The control rod 189 (see FIGURE 3) is oscillated to effect control of the rate of fuel delivery by the pump units 157 by pressure responsive means connected to the previously-mentioned air intake horn 43 through which combustion air is supplied to the crankcases 29. The air horn 43 is mounted on the engine block 24 and comprises, as shown best in FIGURE 5, a hollow member having a throat 291 with the disklike throttle valve 45 mounted therein and operably by suitable remote means, including a control linkage (not shown), to effect speed regulation of the engine 13. The throttle valve controlling linkage is also connected with the distributor 23 by a sub-linkage (not shown) to effect spark advancement and retardation in accordance with the throttle setting. Although more than one air horn can be employed for supplying combustion air through suitable reed valves 41 to the crankcases 29, a single composite air horn is preferably employed in order to reduce fluctuations in air flow and corresponding fluctuations in the pressure condition in the air horn, which pressure condition is employed to actuate the control rod 189 governing the rate of fuel delivery to the injection nozzles 51.

More specifically, the rate of air fiow through the air horn 43 into the crankcases 29 results from reciprocation of the engine pistons and is proportional to the throttle setting or position and to the engine speed. Such air flow creates, in the air horn throat 291, a vacuum or subatmospheric pressure condition which varies proportionally with the rate of air flow. Thus, an increase in engine speed produces increased air flow and an accompanying decrease in pressure in the throat of the air horn. This variation in pressure is employed through a control 6 device 305 and connected linkage to actuate the control rod 189 to provide for injection of relatively small amounts of fuel into the engine cylinders 25 when the engine 13 is operating at relatively low speeds, and to provide for injection of relatively large amounts of fuel into the engine cylinders 25 when the engine 13 is operating at relatively high speeds. In general, the pressure responsive control device 305 and associated linkage is designed and operates to provide a substantially constant air-to-fuel ratio throughout the engine speed range.

Sensing of the pressure condition in the throat 291 of the air horn 43 is enabled by a series of orifices 293, 295, and 297 communicating with the throat 291 and through a passageway 298 with a nipple 299 (see FIG- URE 6). Connected to the nipple 299 is a conduit or line 301 which, in turn, is connected to a vacuum operated control device 305 (see FIGURE 7) which is mounted on a bracket 307 (see FIGURE 3) supported by the injection pump housing 155.

The control device 305 comprises a housing or shell 309 (see FIGURE 7) generally enclosing a chamber 311 which is air-tight except for connection to the line or conduit 30*1 terminating at the air horn throat 291. Thus, the pressure condition in the chamber 311 is a reflection of the pressure condition in the air horn throat.

The shell 30-9 is generally constructed of two parts 315 and 317 so that the chamber 311 is defined by the part 315 and by a movable diaphragm or member 319 including a flexible skirt 321 anchored at the joint between the parts 315 and 317. The diaphragm 319 is connected to one end of an arm 323 which passes through an aperture 320 in the shell part 317 and which, at its other end, is pivotally connected to a crank 325 such that pressure responsive movement of the diaphragm is converted into rotary movement of the control rod 189.

The diaphragm 319 also includes an enlarged, reinforced central portion 327 having a back-up plate 329 fixed on the chamber side thereof, which plate includes a peripheral lip 331 extending inwardly of the chamber. The back-up plate 329 serves as one seat for a spring 333 which is confined Within the chamber 311 and serves to bias the diaphragm 319 in such direction as will rotate the control rod in the clockwise direction as seen in FIG- URE 7, there-by reducing the fuel flow rate to the injection nozzles 51. The other side of the central diaphragm portion 327 includes a recess 335 forming a seat for a second counter-balancing spring 337 which, at its other end, is disposed in a seat formed around the aperture 320 in the shell part 317. Thus, the springs 333 and 337 operate in opposition to each other and serve to stabilize the diaphragm against erratic movement While permitting smooth diaphragm movement in response to pressure changes in the chamber 311.

Preferably, the connecting arm 323 incorporates means, indicated at 339, for adjusting the length thereof, whereby the relative rate of fuel delivery from the pump units can be adjusted when the diaphragm 319 is in its closed throttle position.

Auxiliary fuel pump The fuel supply to the reservoir 177 in the fuel injection pump 17 is preferably maintained under pressure by the auxiliary pump 111 which, in the disclosed construction, is of the diaphragm type. More specifically, the auxiliary fuel pump 111 serves to pump fuel through the filter 115, and through a supply conduit 411 leading from the filter 115 to the fuel inlet port and eventually to the fuel injection pump reservoir 177. In addition, the auxiliary fuel pump serves, as already mentioned, to pump fuel from the fuel storage tanks (not shown) through the conduit or line 113.

The auxiliary fuel pump 111 includes a sub-housing 4-13 joined to the main housing 151 and including a pair of cavities 415 which provide pumping chambers Extending transversely of the bore 154 in the main housing 151 is a cylindrical opening 417 rotatably supporting a rotor or element 419 which is driven incident to rotation of the auxiliary driveshaft 47 by reason of a gear formation 421 on the central part of the rotor 419 and a worm 423 (see FIGURE 3) on the auxiliary driveshaft 47 enmeshed with the gear formation 421. The rotor 419 includes, at each end, an eccentric hub 425 which, during rotation of the rotor, effects pumping operation of a pair of diaphragrns 427 acting in the cavities 415. The cavities 415 communicate with voids 435 in the housing 151, which voids extend radially of the cylindrical opening 417.

In the specifically disclosed construction, the diaphragms 427 are each formed from portions of several layers of flexible, fiuid impervious material, which are secured between the main housing 151 and the sub-housing 413. In addition, each of the diaphragms 427 is confined between supporting plates 429 and 431 of lesser size. Each of the supporting plates 429 is fixed to a separate push rod 433, which rods extend through the voids 435 in the main housing 151 and include elongated slots 430 in which are received eccentric hubs 425 at the ends of the rotor 419. Preferably,the hubs 419 are diametrically oppositely located to provide a generally continuous pumping action.

Each of the diaphragms 427 is biased toward its associated cavity 415 to displace fuel therefrom by a spring 437 confiend between a seat 439 in the void 435 housing the associated push rod 433 and the adjacentassociated supporting plate 429. Thus, during rotation of the rotor, the hubs 425 serve to displace the push rods 433 in one direction against the action of the springs 437, i.e., to withdraw the diaphragms 427 from the cavities 415, while the springs urge the diaphragms 427 in the other direction, i.e., into the cavities to thereby effect pumping of the fuel.

The sub-housing 413 also includes, in association with each of the cavities, separate pairs of check valves. More particularly, each pair of check valves includes an intake valve 441 which operates, incident to creation of a low pressure condition in the associated one of the cavities 415, to connect the associated cavity through a passageway 443 in a plate member 445 to a supply passageway 447 in the sub-housing 413, which passageway connects with the fuel supply conduit 1 13. The other or discharge valve 449 in each pair operates, incident to the creation of a positive pressure condition in the associated one of the cavities, to connect the associated cavity through a passageway 451 in the plate member 445 to the before-mentioned filter 115.

The filter 115 includes a filter housing 461 which is suitable attached to the plate member 445 and supports, in spaced parallel relation, two filter plates 463 of sintered, porous material which permits passage of fuel and prevents passage of grit. Passage of fuel around the edges of the filter plates is prevented by gaskets 465 which are retained in place by the attachment of one side of the filter housing 461 to the plate member 445 and by the attachment of a cover plate 467 to the other side of the filter housing. In the disclosed construction, several bolts 469 are employed to collectively attach the cover plate 467, the filter housing 461, the plate member 445, and the sub-housing 413 to the main housing 151.

In order to take advantage of the full face area of each of the filter plates 463, the surfaces of the plate member 445 and of the cover plate 467 adjacent to the filter housing 461 include recesses 471 and there is provided, through the filter housing 461, a bore 473 permitting fuel flow between the recesses 471' in the plate member 445'and the cover plate 467. Extending from the filter housing 461 from between the filter plates 463 is a nipple 475 which is connected to the conduit 411 leading to the fuel injection pump 17.

.8 The lubricating system The lubricating supply system includes a primary or circulating pump 501 (see FIGURE 3) which functions to maintain a flow of oil from an oil storage tank (not shown), through an oil filter 503, through the fuel injection pump 17, through the main housing 151, and back to the oil storage tank (not shown). The lubricating system also includes the before-mentioned oil injection pump 21 which is located in the main housing 151 and which functions to deliver predetermined quantities of oil to each of the engine cylinders 25.

More particularly, the primary oil pump 50-1 comprises a gear pump including a pair of gears 505 and 507 which are mounted in the main housing 151 in meshed relation to each other and which are driven by the auxiliary driveshaft 47. The suction or intake .side or end of the gear pump 501 is connected through a passageway 506 to an oil inlet 508 which, in turn, is connected through a supply conduit 509 to the oil storage tank (not shown). The pressure side of the gear pump 501 is connected to the intake of the oil filter 593 through a passageway 504 in the main housing 151, and the fuel injection housing 155. In turn, the discharge end of the oil filter 503 is connected to the oil supply port 173 of the fuel injection housing 155. From the supply port 173, the oil flows through the central bore 167, into the transverse recess 169 housing the gears and 187, and into the recess 225 in the main housing 151, which recess contains the timing cam 165. From the recess 225, the oil flows through passageway 434 (see FIGURE 10) into the voids 435 housing the auxiliary fuel pump push rods 433. Suitable conduits still to be described carry oil from the recess 225 and the voids 435 to the oil injection pump 21. From the voids 435, the oil flows through a return nipple 438 which, in turn, is joined to an oil return conduit 440 connected to the oil storage tank (not shown).

The oil injection pump Supply'of oil to each of the engine cylinders 25 is controlled by the oil injection pump 21 which includes a pair of related, but separate, port and piston arrangements each serving two of the engine cylinders 25. Each port and piston arrangement is similar in certain aspects to the oil pumping arrangement set forth in the Trapp and Haft copend-ing application, Serial No. 190,661, now Patent No. 3,144,095, which application is assigned to the assignee of this application. Each port and piston arrangement includes an element or member incorporating a cylinder or bore providing a pumping chamber, a piston in the cylinder, means for reciprocating the piston, together with a valve or port system including a fluid or flow passageway leading from the pumping chamber and coupled with inlet and dischange ports located for successive communication with the fluid passageway.

In the disclosed construction, both of the port and piston arrangements are advantageously incorporated in the rotor 419 which also serves as a component of the auxiliary fuel pump 111. More specifically, in the disclosed construction, the rotor 419 includes, at each end, a pumping cylinder 551 provided with a piston 553 having a spherical outer end which co-operates with components, still to be described, for effecting piston reciprocation incident to rotation of the rotor, as seen in FIGURE 4. The upper piston has been marked 553a and the lower piston has been marked 55%. The other end or pumping face of each of the pistons 553, together with the cylinder walls, defines a pumping chamber having a volume which varies in accordance with reciprocation of the associated piston.

Reciprocation of the pistons 553 is caused, incident to rotation of the rotor 419, by means including a camming plate or end cap 555 at each end of the rotor 419 in position for engagement with the semi-spherical end of the adjacent piston 553 to cause reciprocation thereof. As each pumping chamber or cylinder is intended to feed two engine cylinders, the associated piston 553 is caused to reciprocate twice for each full rotation of the rotor 419 by inclusion on each camming plate of a diametric camming ridge 557 which causes displacement of the associated piston 553 inwardly of the cylinder 551 and defines, on each side thereof, a recessed area 559 permitting movement of the adjacent piston 553 outwardly of the associated cylinder 551.

The piston reciprocation means further includes eccentric disposition of the ends of the cylinders 551 so that the semi-spherical piston end will encounter the camming ridge 557 at points spaced from the axis of rotor rotation, thereby to effect the desired reciprocation by displacing the pistons inwardly of the cylinders and permitting subsequent outward movement. In the particularly disclosed construction, the cylinders 551 form end portions of a bore 561 extending obliquely through the rotor 419, terminating at the outer end faces of the hubs 425.

If each piston and port arrangement is intended to serve three or more cylinders, rather than two cylinders, then the camming plate could be designed with three or more ridge portions as desired.

The piston reciprocation means can employ various arrangements for effecting displacement of the pistons 553 outwardly of the pumping cylinders 551. For instance, an outwardly acting spring could be employed in the pumping chamber. In the disclosed construction, outward movement of one piston is effected by inward movement of the other piston so that, in effect, there is positive reciprocation of the pistons 553 in both directions. Such co-ordinated interaction between the pistons is provided by locating opposed camming plates 555 with their respective camming ridges in angularly spaced relation to each other to permit outward movement of one piston While the other piston is displaced inwardly, and by forming the elongated bore 561 with a reduced central portion 563 housing a blocking means in the form of a plunger assembly 565 which wholly occupies the cross sectional area of the reduced bore portion 563 to prevent oil flow therethrough and which reciprocates in response to action of the camming ridges 557 with the pistons 553.

In the specifically disclosed construction, the plunger assembly 565 includes two plungers 567 each incorporating oposing stub shafts 569 and a coil spring 571 which is interposed between the plungers in telescopic relation around the stub shafts 569 to accommodate variation in manufacture. As is also shown, the outer end of each of the plungers 567 is conically tapered and is engaged with the pumping face of the adjacent piston 553.

The port arrangement associated with each piston 553 includes a flow passageway 573 (see FIGURE 4) leading from the associated pumping chamber to the outer surface of the rotor 419 in position to communicate with a pair of supply or intake ports 575 and 577 and a pair of outlet or discharge ports 579 and 581. Specifically, as seen best in FIGURE 9, the pair of intake ports 575a and 577a associated with the pistons 553a are diametrically oppositely located with respect to each other, while the pair of discharge ports 57% and 581a are also diametrically oppositely located intermediate the supply ports 575a and 577a. The intake ports 575a and 5770 respectively communicate with the recess 225 housing the fuel injection timing cam 165 and with one of the voids 435 housing the auxiliary fuel pump push rods 433. The discharge ports 579a and 581a respectively terminate at fittings 585 and 587, to which are connected separate supply tubes 57 leading to the individual engine cylinders 25.

A duplicate port arrangement is employed with the other piston 553b to eflfect supply of oil to the pair of engine cylinders in the other cylinder bank in the engine 13. However, because one piston reciprocates inwardly discharging oil into one of the outlet ports, while the other piston reciprocates outwardly drawing oil to the associated pumping chamber 551 through one of the inlet ports, the port arrangements are angularly offset with respect to each other. More specifically, as seen in FIGURE 10, the port arrangement associated with the piston 553b includes supply or intake ports 57512 and 577b respectively communicating with the recess 225 and with the other one of the voids 433. The discharge ports 579i; and 5811: respectively terminate at fittings 589 and 591, which fittings are connected to tubes 57 leading to the individual engine cylinders 25.

If it is desired to employ the disclosed oil pumping arrangement with a six cylinder or eight cylinder engine, with each piston and port arrangement serving one-half of the total cylinders, the port arrangement can be modified to include three or four intake ports and three or four discharge ports for each piston.

Each of the oil fittings 55 constitutes, in part, an opening in the wall of the associated cylinder 25, located so as to be in opposed relation to the skirt of the piston when the piston is at or near bottom dead center. The location of the intake and discharge ports with relation to the fiow passageway 573 in the rotor 419, coupled with the connection between the worm 423 and gear formation 421, provides for injection of a slug of oil in each cylinder for every any twenty revolutions and for said injection to take place while the piston is preferably at or near bottom dead center. While the number of revolutions per slug can be varied over a wide range, injecting the oil when the piston is at bottom dead center has particular advantages. Such injection results in the application of oil to the piston skirt and, as a result, oil is delivered along the wall of the cylinder from the skirt in response to piston riciprocation. Oil in excess of the requirement for cylinder lubrication is conducted into the crankcase, is consequently fogged, and is carried to the wrist pin, connecting rod bearings, and other points to be lubricated.

Various of the features of the invention are set forth in the following claims.

What is claimed is:

1. The combination of an engine having a plurality of closed chambers each including a crankcase and a cylinder, a crankshaft extending through said crankcases,

and separate pistons riciprocably movable in each of said cylinders and connected to said crankshaft, an auxiliary shaft connected to said crankshaft for rotation in timed relation to said crankshaft,

a fuel injection pump driven by said auxiliary shaft and communicating with a source of fuel, said fuel injection pump including a plurality of pumping units equal in number to the number of cylinders, each pumping unit being connected with one of said cylinders so as to inject fuel into said cylinders in timed relation to the movement of said pistons in said cylinders, and

an oil injection pump driven by said auxiliary shaft and communicating with a source of oil, said oil injection pump including means for delivering oil separately to each of said cylinders in common timed relation to the movement of said pistons in said cylinders.

2. A fuel injection and oil pumping device adapted to be used with a multi-cylinder internal combustion engine, said device comprising a housing,

a driveshaft rotatably supported by said housing,

a series of fuel injection pump units carried by said housing in parallel disposition With said driveshaft and at a common radius therefrom,

a driving cam on said driveshaft in operable engagement with said pump units to effect successive fuel 1 1 discharging operation thereof in response to rotation of said driveshaft,

an oil pumping cylinder in said housing,

a piston reciprocable in said cylinder, and

means connecting said piston and said driveshaft for reciprocating said piston in response to rotation of said driveshaft, whereby the co-ordinated pumping of oil and fuel is effected.

3. A device in accordance with claim 2 incombination with a circulating oil system including an oil circulating pump supported by said housing and adapted for communication with a source of oil,

an oil filter communcating with said oil circulating pump for receiving a flow of oil therefrom,

conduit means connectiing said filter to said pumping units, to said driving cam, to saiddriveshaft and to said pumping cylinder, and

means in communication with said conduit means and adapted for communication with means for returning oil to said oil source.

4. A device in accordance with claim 2 including pressure responsive means adapted to be connected to the combustion air intake of an engine for effecting a common variation in the discharge rate from each of said pump units, said means including means defining a bore in said housing in axial alignment with said driveshaft,

a rotatable rod in said bore, and

means connecting said rod to all of said pump units.

5. A device in accordance with claim 2 including an auxiliary fuel pump supported by said housing and driven by said driveshaft, said auxiliary fuel pump communicating with said fuel injection pump units for supplying fuel thereto from a fuel source.

6. A fuel injection and oil pumping device to be used with a multi-cylinder internal combustion engine, said device comprising a housing having a cylindrical opening therein,

a driveshaft rotatably supported by said housing,

a series of fuel injection pump units carried by said housing in parallel disposition to said driveshaft and at a common radius from the axis thereof,

a driving cam on said shaft in operable engagement with said pump units to effect successive fuel discharging operation thereof in response to rotation of said shaft,

a rotatable element in said opening in driving engagement with said driveshaft and having an eccentric crank thereon,

an oil pumping cylinder,

a piston reciprocably operable in said cylinder,

means for reciprocating said piston in response to rotation of said element,

an auxiliary fuel pump supported by said housing, communicating with said pump units for supplying fuel thereto, and including a reciprocable pumping member, and

means connecting said pumping member and said eccentric crank to effect reciprocation thereof in response to rotation of said element.

7. A device in accordance with claim 6 wherein said eccentric crank is located at an end of said element,

said pumping cylinder terminates at the end face of said crank,

said piston extends from said cylinder,

carrnning means is disposed on said housing in engagement with the outer end of said piston to effect piston displacement inwardly of said cylinder and to permit piston displacement outwardly of said cylinder, and

means-for effecting said outward piston displacement when permitted by said camming means.

8. A combined pumping device including a housing having therein a cylindrical opening, and a recess extending radially of said opening with a closed outer end,

a diaphragm disposed across said recess in spaced relation to said outer end thereof and forming one wall of a pumping chamber,

valve and conduit means communicating with said pumping chamber for effecting flow of fluid to and from said pumping chamber in response to displacement of said diaphragm toward and away from said outer end of said recess,

a rotatable element in said opening including therein a. pump cylinder and having an eccentric crank pin portion,

a rod connecting said diaphragm and said crank pin portion to cause displacement of said diaphragm in response to rotation of said element, a piston in said a pump cylinder,

means for sequentially connecting said. pump cylinder to a fluid inlet line and a fluid outlet line in response to rotation of said element,

means operable in response to rotation of said element for reciprocating said piston in co-ordination with the connection of said pump cylinder to the said inlet and outlet lines, whereby to effect pumping of said fluid from said inlet line to said outlet line, and

means for rotating said element to cause pumping operation of said diaphragm and of said piston.

9. A pumping device in accordance with claim 8 wheresaid crank pin constitutes an eccentric hub at one end of said element, and

said pump cylinder terminates at the end face of said hub.

10. A pumping device in accordance with claim 9 wherein said piston has a concavely formed outer end surface,

and said piston reciprocation means includes stationary camming means on said housing located adjacent said end face, of said hub for engagement with the outer end piston surface including a rib for eifetcing displacement of said piston inwardly of said pump cylinder, and a recessed area permitting displacement of said piston outwardly of said pump cylinder, and means for effecting outward displacement of said pistons.

11. A pumping device in accordance with claim 10 wherein a pair of pump cylinders are provided by end portions of an elongated bore in said element said bore terminating at one end, at said end face of said hub.

12. A combined pumping device including a housing having therein a cylindrical opening and a pair of recesses extending radially of said opening from adjacent the ends thereof, said recesses having closed outer ends,

a diaphragm disposed across each of said recesses in spaced relation to their outer ends to form one wall of a pair of pumping chambers,

valve and conduit means communicating with said pumping chambers for effecting flow of fluid to and from said pumping chambers in response to diaphragm displacement toward and away from said recess outer ends,

a rotatable element in said opening including, at each end, an eccentric hub constituting a crank pin, and a bore extending obliquely of the axis of said ele- 13 ment and terminating at the end faces of said hubs, said bore having a central portion of reduced diameter and including, adjacent each end, a pump cylinder,

rods respectively connected to said crank pins to cause diaphragm displacement in response to rotation of said element,

a piston in each of said pump cylinders,

means for sequentially connecting said pump cylinders to a fluid inlet line and a fluid outlet line in response to rotation of said element,

a stationary camming means on said housing located adjacent the end face of each of said hubs for engagement with the outer ends of said pistons, said camming means each including a rib for effecting displacement of the adjacent one of said pistons inwardly of the adjacent one of said pump cylinders, said ribs being located in angular relation to each other, and a recessed area permitting displacement of said pistons outwardly of said pump cylinders, and

a plunger unit located in said central bore portion to prevent flow therethrough, said plunger unit having its ends in engagement with said pistons and being movable in said central portion in response to inward displacement of said pistons by the associated ribs.

13. A device in accordance with claim 12 wherein said plunger unit includes two plungers, and spring means disposed between said plungers for urging said plungers apart.

14. A pump for delivering predetermined fluid quantities, said pump comprising a housing having a cylindrical opening therein,

a rotatable element in said cylindrical opening, said element including therein a pair of pump cylinders, separate reciprocably movable pistons in each of said pump cylinders,

a separate flow passageway in said element leading from each of said cylinders and terminating on the surface of said element at points spaced axially of the rotational axis of said element,

a separate supply port in said housing communicating with said opening in each of two planes spaced along the rotational axis of said element to provide communication with said spaced flow passageways,

-a separate discharge port in said housing communicating with said opening in each of said two spaced planes to provide communication with said spaced flow passageways, said discharge port in each of said planes being in angularly offset relation with respect to said supply port therein, means for reciprocating said pistons incident to rotation of said element in co-ordination with the communication between said flow passageways and said supply and discharge ports so as to effect pumping, and means on said housing for rotating said element. 15. A pump in accordance with claim 14 wherein each of said pump cylinders has an open end terminating at an end of said element, said pistons have convexly formed outer end surfaces,

and said piston reciprocation means includes stationary camming means on said housing located adjacent to each of said open ends of said pump cylinders for engagement with said outer end piston surfaces, each of said camming means including a rib for effecting displacement of the adjacent one of said pistons inwardly of the associated one of said pump cylinders, and a recessed area permitting displacement of the adjacent one of said pistons outwardly of the associated one of said pump cylinders.

16. A pump in accordance with claim15 wherein said pump cylinders are provided by end portions of an elongated bore in said rotatable element terminating at the ends of said rotatable element.

17. A pump in accordance with claim 16 wherein said stationary camming means is located at each end of said cylindrical opening with said ribs in angular relation to each other,

said bore includes a central portion of reduced diameter, and

a plunger unit is located in said central portion to prevent flow therethrough, said plunger unit having its ends in engagement with said pistons, and being axially movable in said central portion in response to inward displacement of one of said pistons by the adjacent rib to effect outward displacement of the other of said pistons into the adjacent recessed area.

18. A pump for delivering predetermined fluid quantities, said pump comprising a housing having a cylindrical opening therein,

supply ports in said housing communicating with said opening in each of two planes spaced along the rotational axis of said element, said supply ports being located with the supply port in one of said planes in angularly offset relation with respect to the supply port in the other of said planes,

a discharge port in said housing communicating with said opening in each of said two spaced planes, said discharge port in each of said planes being in angularly offset relation with respect to said supply port therein,

a rotatable, elongated element in said opening in said housing, said element including a lengthwise bore extending obliquely to the rotational axis of said element, and a pair of axially spaced flow passageways positioned for communication with said ports in said spaced planes,

fluid blocking means in said bore between said flow passageways,

means on said housing for rotating said element,

separate reciprocably movable pistons in said bore at each end thereof, and

separate endcaps on said housing at each of the ends of said opening in engagement with the adjacent one of said pistons, said endcaps each having means defining a rib extending radially of the rotational axis of said element for engagement with the end of the adjacent one of said pistons, said ribs being angularly offset with respect to each other, whereby said pistons are reciprocated in response to rotation of said element.

19. A fuel pump for a fuel injection system for a multi-cylinder, internal combustion engine, said pump comprising a housing including means defining an elongated bore in said housing, and a plurality of pump cylinders arranged in parallel relation to said elongated bore and at a common radial distance from said bore, separate liners in each of said cylinders, each of said liners including means adapted for communicating with a source of fuel, and a discharge port, separate pistons reciprocably movable in each of said liners, each of said pistons and the associated one of said liners being oscillatable relative to each other about the axis of the associated one of said pump cylinders to effect variation in the quantity of fuel discharged therefrom in response to' piston reciprocation, means for reciprocating said pistons in said respective liners through a predetermined stroke length so as to cause discharge through said ports of preselected amounts of fuel, and

means in said axial bore and connected to one of each associated pair of said pistons and said liners for effecting common relative oscillation between said pistons and said liners so as to preselect the quantity of fuel discharged through said ports in response to piston reciprocation.

20. A fuel pump in accordance with claim 19 wherein means is provided for restraining said pistons against rotation, and

said oscillation effecting means includes a rotatable rod in said axial bore, an actuating gear on said rod, and separate gears on each of said liners enmeshed with said actuating gear.

21. A fuel pump an accordance with claim 19 wherein fluid pressure responsive means is connected to said oscillation effecting means to control operation thereof, said fluid pressure responsive means being adapted to communicate with the combustion air intake of said engine so as to reflect pressure change occurring therein incident to control of engine speed.

22. A fuel pump in accordance with claim 19 wherein each of said pistons supports a roller for rotation about an axis extending radially of said central bore, and

said piston reciprocating means includes a timing cam supported for rotation about an axis in alignment with the axis of said bore and disposed in engagement with said rollers, said cam having thereon means for effecting successive reciprocation of said pistons incident to rotation of said cam, and means for rotating said cam.

23. The combination of p a multi-cyclinder engine having at least two separate chambers each including a cylinder portion and a crankcase portion extending from said cylinder portion,

separate sparkplugs in each of said cylinder portions, and I 7 separate pistons reciprocably movable in each of said cylinder portions,

a shaft connected to said engine and rotated, during operation of the engine, in timed relation to the firing of said spark plugs,

a distributor driven by said shaft and electrically connected to said spark plugs, whereby the firing order of said spark plugs is established, a fuel injection pump driven by said shaft and communicating with a source of fuel and separately with each of said cylinder portions so as to inject fuel into said cylinder portions in timed relation to the firing of said spark plugs, and

an oil injection pump driven by said shaft and communicating with a source of oil and separately with cylinder portions so as to inject fuel into said chambers in timed relation to the firing of said spark plugs.

24. The combination of an engine having an engine block incorporating a plurality of cylinders,

separate spark plugs in each of said cylinders, and

separate pistons reciprocably movable in each of said cylinders,

a shaft connected to said engine and rotated, during operation, of the engine, in timed relation to the firing of said spark plugs,

a distributor driven by said shaft and electrically connected to said spark plugs, whereby the firing order of said spark plugs is established,

a fuel injection pump driven by said shaft and communicating with a source of fuel and separately with each of said cylinders so as to inject fuel into said cylinders in timed relation to the firing of said spark plugs, and

:an oil injection pump driven by said shaft and communicating with .a source of oil and separately with each of said cylinders so as to deliver oil to said cylinders in timed relation to the firing of said spark plugs.

25. In an engine assembly having a plurality of cylinders, separate pistons reciprocably movable in each of said cylinders, and a crankshaft connected to said pistons for co-ordinating the movement thereof, the improvement comprising a dual fuel and oil pumping unit connected to said engine and including an auxiliary driveshaft drivingly connected to said crankshaft for rotation in timed relation to said crankshaft,

a fuel injection pump driven by said auxiliary driveshaft and communicating with a source of fuel, said fuel injection pump including a plurality of pumping units equal in number to the number of cylinders, each pumping unit being connected with one of said cylinders so as to inject fuel into said cylinders in timed relation to the movement of said pistons, and 1 an oil injection pump driven by said auxiliary driveshaft and communicating with a soure of oil, said oil injection pump including means for delivering oil separately to each of said cylinders in common timed relation to the movement of said pistons, v I

26. In an engine assembly having a cylinder, a combustion air intake communicable with said cylinder, a piston reciprocably movable in said cylinder, and a crankshaft connected to said piston, the improvement comprisa dual fuel and oil pumping unit connected to said engine and including d an auxiliary drive shaft drivingly connected to said crankshaft for rotation in timed relation to said crankshaft,

a fuel injection pump driven by said auxiliary driveshaft and communicating with a source of fuel and.with said cylinder so .as to inject fuel in variable quantities into said cylinder in timed relation to the movement of said piston,

an oil injection pump. driven by said auxiliary driveshaft and communicating with a source of oil and with said cylinder so as to deliver oil to said cylinder in timed relation to the movement of said piston, and

pressure responsive means communicating with said combustion air intake and connected to said fuel injection pump for varying the quantitative rate of fuel discharged from said pump in response to changes in the pressure condition in said combustion air intake.

27. The combination of an engine having a plurality of generally closed chambers each including a cylinder, a crankcase, and an oil fitting, a piston reciprocable in each of said cylinders, a common crankshaft extending in each of said crankcases and operatively connected to each of said pistons, an auxiliary driveshaft drivingly connected to said crankshaft for rotation in timed relation to said crankshaft, a fuel injection pump driven by said auxiliary driveshaft and communicating with a source of fuel and with said cylinders in timed relation to piston movement, and an oil injection pump driven by said auxiliary driveshaft and including means communicating with a source of oil and separately with each of said oil fittings for separately metering oil to said chambers in timed relation to piston movement.

28. The combination of an engine including a pair of generally closed chambers each including a cylinder, and means defining an oil fitting, separate pistons reciprocal in each of said cylinders, and a common crankshaft extending through said chambers and connected to each of said pistons, an oil pump for delivering predetermined fluid quantities of oil, said pu'mp comprising a housing having a cylindrical opening therein, a rotatable element in said cylindrical opening, said element including therein a pair of pump cylinders, separate reciprocably movable pistons in each of said pump cylinders, a separate flow passageway in said element leading from each of said pump cylinders and terminating on the surface of said element at points spaced axially of the rotational axis of said element, separate supply ports in said housing communicating with said opening in each of two planes spaced along the rotational axis of said element to provide communication with said spaced flow passageways, a separate discharge port in said housing communicating with said opening in each of said two spaced planes to provide communication with said spaced flow passageways, said discharge port in each of said plane-s being in angularly offset relation with respect to said supply port therein, means for reciprocating said pistons incident to rotation of said element in coordination with the communication between said flow passageways and each of said supply and discharge ports so as to eifect pumping, and means connected to said crankshaft and to said element for rotating said element in timed relation to rotation of said crankshaft, and separate con duit means connecting each of said discharge ports to said oil fittings whereby said oil pump is operable to pump oil directly to each of said closed chambers.

29. The combination of an engine having a cylinder, a piston reciprocable in said cylinder, a crankshaft operatively connected to said piston, and means for separately introducing fuel and oil into said cylinder in timed relation to piston movement and including a fuel injection pump communicating with a source of fuel and with said cylinder, an oil injection pump communicating with said cylinder, and a circulatory oil supply system including an oil circulating pump having an inlet adapted for communication with a source of oil and an outlet, an oil filter communicating with said outlet of said oil circulating pump and with said oil injection pump, and means communicating with said outlet of said oil circulating pump and adapted for communication with the oil source for returning to the oil source any oil in excess to the operation of said oil injection pump.

30. The combination of an engine having a plurality of cylinders, a piston reciprocable in each of said cylinders, a crankshaft operatively connected to said pistons, and means for separately introducing fuel and oil into said cylinders in timed relation to piston movement and including an auxiliary driveshaft drivingly connected to said crankshaft for rotation in timed relation to said crankshaft, a fuel injection pump driven by said auxiliary driveshaft and communicating with a source of fuel and separately with each of said cylinders, said fuel injection pump including a series of pump units, one for each cylinder, means supporting said pump units in parallel disposition to said auxiliary driveshaft at a common radius from the axis of said auxiliary driveshaft, and in equi-angularly spaced relation to one another about said auxiliary driveshaft axis, and an oil injection pump, driven by said auxiliary driveshaft, and communicating with a source of oil, and separately with each of said cylinders.

31. A combination in accordance with claim 30 including means connected to all of said pump units to effect a common variation in the discharge rate from each of said pump units, said means being pressure responsive and communicating with the combustion air intake of said engine.

32. A combined oil and fuel pumping device including a housing having therein means defining a cylindrical opening, means defining a recess extending radially of said opening with a closed outer end, means defining an elongated bore and means defining a plurality of fuel pumping cylinders arranged in parallel relation to said elongated bore and at a common radial distance from said bore, a diaphragm disposed across said recess in spaced relation to said outer end thereof and forming one wall of a fuel pumping chamber, valve and conduit means communicating with said fuel pumping chamber for effecting flow of fuel to and from said fuel pumping chamber in response to displacement of said diaphragm toward and away from said outer end of said recess, a rotatable element in said opening including therein an oil pumping cylinder and having an eccentric crank pin portion, a rod connecting said diaphgram and said crank pin portion to cause displacement of said diaphragm in response to rotation of said element, an oil pumping piston in said oil pumping cylinder, means for sequentially connecting said oil pumping cylinder to an oil inlet line and an oil outlet line in response to rotation of said element, means operable in response to rotation of said element for reciprocating said oil pumping piston in coordination with the connection of said oil pumping cylinder to the said oil inlet and oil outlet lines, whereby to effect pumping of oil from said oil inlet line to said oil outlet line, separate liners in each of said fuel pumping cylinders, each of said liners including means communicating with said fuel pumping chamber and a fuel discharge port, separate fuel pumping pistons reciprocably movable in each of said liners, each of said fuel pumping pistons and the associated one of said liners being oscillatable relative to each other about the axis of the associated one of said fuel pumping cylinders to effect variation in the quantity of fuel discharge therefrom in response to fuel pumping piston reciprocation, means for reciprocating said fuel pumping pistons in said respective liners through a predetermined stroke length so as to cause fuel discharge through said fuel discharge ports of preselected amounts of fuel, and for rotating said element to cause fuel pumping operation of said diaphragm and oil pumping operation of said oil pumping piston, and means in said axial bore and connected to one of each associated pair of said fuel pumping pistons and said liners for effecting common relative oscillation between said fuel pumping pistons and said liners so as to preselect the quantity of fuel discharge through said fuel discharge ports in response to fuel pumping piston reciprocation.

33. A combined pump for a multi-cylinder, internal combustion engine, said pump comprising a housing including means defining an elongated bore in said housing, means defining a cylindrical opening in said housing, and means defining a plurality of pump cylinders in said housing arranged in parallel relation to said elongated bore and at a common radial distance from said bore, separate liners in each of said pump cylinders, each of said liners including means adapted for communicating with a source of fuel and a fuel discharge port, separate fuel pumping pistons reciprocably movable in each of said liners, each of said fuel pumping pistons and the associated one of said liners being oscillatable relative to each other about the axis of the associated one of said pump cylinders to effect variation in the quantity of fuel discharge therefrom in response to fuel pumping piston reciprocation, a rotatable element in said cylindrical opening, said element including therein a pair of pumping cylinders, separate reciprocably movable oil pumping pistons in each of said pumping cylinders, a separate flow passageway in said element leading from each of said pumping cylinders and terminating on the surface of said element at points spaced axially of the rotational axis of said element, a separate supply port in said housing communicating with said opening in each of two planes spaced along the rotational axis of said element to provide communication with said spaced flow passageways, a separate oil discharge port in said housing communicating with said opening in each of said two spaced planes to provide communication with said spaced flow passageways, said oil discharge port in each of said planes being in angularly offset rleation with respect to said supply port therein, means for reciprocating said oil pumping pistons incident to rotation of said element in coordination with the communication between said flow passageways and said oil' supply and discharge ports so as to effect pumping, means on said housing for rotating said element so as to cause oil discharge through said oil discharge ports and for reciprocating said fuel pumping pistons in said respective liners through a predetermined stroke length so as to cause fuel discharge through said fuel discharge ports of preselected amounts of fuel, and means in said axial bore and connected to one of each associated pair of said fuel pumping pistons and said liners for effecting common relative oscillation between said fuel pumping pistons and said liners so as to preselect the quantity of fuel discharge through said fuel discharge ports in response to fuel pumping piston reciprocation.

34'. The combination of an engine having a cylinder, a piston reciprocable in said cylinder, a crankshaft operatively connected to said piston, and means for separately introducing fuel and oil into said cylinder in timed rela-' tion to piston movement and including a housing having therein means defining a cylindrical opening, and a recess extending radially of said opening with a closed outer end, a diaphragm disposed across said recess in spaced relation to said outer end thereof and forming one wall of a pumping chamber, valve and conduit means communicating with said pumping chamber and with a' source of fuel for effecting fuel flow to and from said pumping chamber in response to displacement of said diaphragm toward and away from said outer end of said recess, a rotatable element in said opening including therein a pump cylinder and having an eccentric crank pin portion, a rod connecting said diaphragm and said crank pin portion to cause displacement of said diaphragm in response to rotation of said element, a piston in said pump cylinder, means for sequentially connecting said pump cylinder to an oil inlet line communicating with a source of oil and an oil outlet line communieating with said cylinder in response to rotation of said element, means operable in response to rotation of said element for reciprocating said piston in co-ordination with the connection of said pump cylinder to the said inlet and outlet lines, whereby to effect pumping of said oil from said inlet line to said outlet line, a fuel injection pump communicating with said pumping chamber and with said cylinder, and an auxiliary driveshaft drivingly connected to said crankshaft for rotation in ti-med relation to said crankshaft, drivingly connected to said fuel injection pump for effecting operation thereof, and drivingly connected to said element for effecting rotation thereof.

35. The combination of an engine having a pair of cylinders, a piston reciprocable in each of said cylinders, a crankshaft operatively connected to said pistons, and means for separately introducing fuel and oil into said cylinders in timed relation to piston movement and including an auxiliary driveshaft drivingly connected to said crankshaft for rotation in timed relation to said crankshaft, a fuel injection pump driven by said auxiliary driveshaft and communicating with a source of fuel and separately with each of said cylinders, and an oil injection pump comprising a housing having therein means defining a cylindrical opening, a rotatable element in said cylindrical opening, said element including therein a pair of pump cylinders, separate reciprocably movable pistons in each of said pump cylinders, a separate flow passageway in said element leading from each of said cylinders and terminating on the surface of said element at points spaced axially of the rotational axis of said element, supply ports in said housing respectively communicating with a source of oil and with said opening in each of two planes spaced along the rotational axis of said element to provide communication with said spaced flow passageways, a separate discharge port in said housing communicating with said opening in each of said two spaced planes to provide communication with said spaced flow passageways, said discharge port in each of said planes being in angularly offset relation with respect to said supply port therein, said discharge ports communicating separately with said cylinders, means for reciprocating said pistons incident to rotation of said element in co-ordination with the communication between said flow passageways and said supply and discharge ports so as to effect pumping, and means drivingly connecting said auxiliary driveshaft and said element for rotation of the latter in response to rotation of the former.

36. The combination of an engine having a plurality of cylinders, separate pistons reciprocable in each of said cylinders, a crankshaft operatively connected to said pistons, and means for separately introducing fuel and oil into said cylinders in timed relation to piston movement and including an auxiliary driveshaft drivingly connected to said crankshaft for rotation in timed relation to said crankshaft, a fuel injection pump and an oil injection pump driven by said auxiliary driveshaft and communicating with a source of oil and separately with each of said cylinders, a fuel injection pump comprising a housing including means defining an elongated bore in said housing, and a plurality of pump cylinders arranged in parallel relation to said elongated bore and at a common radial distance from said bore and corresponding in number to the number of said cylinders, separate liners in each of said cylinders, said liners each including means adapted for communication with a source of fuel, and each including a discharge port communicating separately with one of said cylinders, separate pistons reciprocably movable in each of said liners, each of said pistons and the associated one of said liners being oscillatable relative to each other about the axis of the associated one of said pump cylinders to effect variation in the quantity of fuel discharged therefrom in response to piston reciprocation, means drivingly connecting said auxiliary driveshaft and said pistons for reciprocating saidpistons in said respective liners through a predetermined stroke length so as to cause discharge through said ports of preselected amounts of fuel, and means in said axial bore and connected to one of each associated pair of said pistons and said liners for effecting common relative oscillation between said pistons and said liners so as to preselect the quantity of fuel discharge through said ports in response to piston reciprocation.

37. A combined pumping device including a housing having therein means defining a cylindrical opening, and a recess extending radially of said opening with a closed outer end, a diaphragm disposed across said recess in spaced relation to said outer end thereof and forming one wall of a pumping chamber, valve and conduit means communicating with said pumping chamber for effecting fluid flow to and from said pumping chamber in response to displacement of said diaphragm toward and away from said outer end of said recess, a rotatable element in said opening, said element including therein a pair of pump cylinders, and having an eccentric crank pin portion, a rod connecting said diaphragm and said crank pin portion to cause displacement of said diaphragm in response to rotation of said element, separate reciprocably movable pistons in each of said pump cylinders, a separate flow passageway in said element leading from each of said cylinders and terminating on the surface of said element at points spaced axially of the rotational axis of said element, a separate supply port in said housing communicating with said opening in each of two planes spaced along the rotational axis of said element to provide communication with said spaced flow passages ways, a separate discharge port in said housing com municating with said openings in each of said two spaced planes to provide communication with said spaced flow passageways, said discharge port in each of said planes being in angularly offset relation with respect to said supply port therein, means for reciprocating said pistons incident to rotation of said element in co-ordination with the communication between said flow passageways and said supply and discharge ports so as to eifect pumping, and means on said housing for rotating said element to cause pumping operation of said diaphragm and of said piston.

38. The combination of an engine having a plurality of closed chambers each including a crankcase, a cylinder, a piston reciprocable in said cylinder, and an oil fitting, a common crankshaft operatively connected to said pistons, and means for separately introducing fuel and oil into said cylinders in timed relation to piston movement and including an auxiliary driveshaft drivingly connected to said crankshaft for rotation in timed relation to said crankshaft, a fuel injection pump driven by said auxiliary driveshaft and communicating with a source of fuel and separately with each of said cylinders, an oil injection pump driven by said auxiliary driveshaft and communicating with a source of oil, and separate conduits leading from said oil pump to each of said oil fittings, whereby oil is pumped directly from said oil pump to said closed chambers.

39. The combination of an engine having a cylinder, a piston reciprocable in said cylinder, and a crankshaft operatively connected to said piston, and an integrated pumping unit mounted on said engine for separately introducing fuel and oil into said cylinder in timed relation to piston movement and including an auxiliary drive shaft drivingly connected to said crankshaft for rotation in timed relation to said crankshaft, a fuel injection pump driven by said auxiliary driveshaft and communicating with said cylinder, an auxiliary fuel pump driven by said auxiliary driveshaft and communicating with a source of fuel, conduit means connecting said auxiliary fuel pump to said injection fuel pump, and an oil injection pump driven by said auxiliary driveshaft and communicating with a source of oil and with said cylinder.

40. The combination of an engine including a plurality of generally closed chambers each including a cylinder, separate pistons reciprocable in each of said cylinders, a common crankshaft to which each of said pistons is connected, an oil pump communicating with a source of oil, an oil fitting in each of said closed chambers, said oil fittings being located in opposing relation to the skirt of the associated one of said pistons when said pistons are located adjacent their bottom dead center position, and separate conduit means connecting said oil pump to each of said oil fittings whereby said oil pump is operable to pump oil directly to each of said closed chambers.

References Cited by the Examiner UNITED STATES PATENTS 1,643,674 9/1927 Miller 184-6 2,159,360 5/1939 Starr et al. 10341.1 2,265,692 12/1941 Kammer 10341.1 2,391,221 12/1945 Beeh 123-13911 2,428,373 10/1947 Lloyd 103--6 2,570,560 10/1951 Katcher 103----6 2,738,861 3/1956 Emele et a1 184 -6 FOREIGN PATENTS 834,533 5/ 1960 Great Britain. 496,711 8/1954 Italy.

MARK NEWMAN, Primary Examiner.

RICHARD B. WILKINSON, Examiner. 

1. THE COMBINATION OF AN ENGINE HAVING A PLURALITY OF CLOSED CHAMBERS EACH INCLUDING A CRANKCASE AND A CYLINDER, A CRANKSHAFT EXTENDING THROUGH SAID CRANKCASES, AND SEPARATE PISTONS RECIPROCABLY MOVABLE IN EACH OF SAID CYLINDERS AND CONNECTED TO SAID CRANKSHAFT, AN AUXILIARY SHAFT CONNECTED TO SAID CRANKSHAFT FOR ROTATION IN TIMES RELATION TO SAID CRANKSHAFT, A FUEL INJECTION PUMP GIVEN BY SAID AUXILIARY SHAFT AND COMMUNICATING WITH A SOURCE OF FUEL, SAID FUEL INJECTION PUMP INCLUDING A PLURALITY OF PUMPING UNITS EQUAL IN NUMBER TO THE NUMBER OF CYLINDERS, EACH PUMPING UNIT BEING CONNECTED WITH ONE OF SAID CYLINDERS SO AS TO INJECT FUEL INTO SAID CYLINDERS IN TIMED RELATION TO THE MOVEMENT OF SAID PISTON IN SAID CYLINDERS, AND AN OIL INJECTION PUMP DRIVEN BY SAID AUXILIARY SHAFT AND COMMUNICATING WITH A SOURCE OF OIL, SAID OIL INJECTION PUMP INCLUDING MEANS FOR DELIVERING OIL SEPARATELY TO EACH OF SAID CYLINDERS IN COMMON TIMED RELATION TO THE MOVEMENT OF SAID PISTON IN SAID CYLINDERS.
 40. THE COMBINATIION OF AN ENGINE INCLUDING A PLURALITY OF GENERALLY CLOSED CHAMBERS EACH INCLUDING A CYLINDER, SEPARATE PISTONS RECIPROCABLE IN EACH OF SAID CYLINDERS, A COMMON CRANKSHAFT TO WHICH EACH OF SAID PISTONS IS CONNECTED, AN OIL PUMP COMMUNICATING WITH A SOURCE OF OIL, AN OIL FITTING IN EACH OF SAID CLOSED CHAMBERS, SAID OIL FITTINGS BEING LOCATED IN OPPOSING RELATION TO THE SKIRT OF THE ASSOCIATED ONE OF SAID PISTONS WHEN SAID PISTONS ARE LOCATED ADJACENT THEIR BOTTOM DEAD CENTER POSITION, AND SEPARATE CONDUIT MEANS CONNECTING SAID OIL PUMP TO EACH OF SAID OIL FITTINGS WHEREBY SAID OIL PUMP IS OPERABLE TO PUMP OIL DIRECTLY TO EACH OF SAID CLOSED CHAMBERS. 